EP0637483B1 - Werkzeug zur Bearbeitung von Werkstücken - Google Patents

Werkzeug zur Bearbeitung von Werkstücken Download PDF

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Publication number
EP0637483B1
EP0637483B1 EP94111435A EP94111435A EP0637483B1 EP 0637483 B1 EP0637483 B1 EP 0637483B1 EP 94111435 A EP94111435 A EP 94111435A EP 94111435 A EP94111435 A EP 94111435A EP 0637483 B1 EP0637483 B1 EP 0637483B1
Authority
EP
European Patent Office
Prior art keywords
tool according
feed
gearing
curved track
fine
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP94111435A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0637483A1 (de
Inventor
Helmut Dipl.-Ing. Dischler
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Individual
Original Assignee
Individual
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Individual filed Critical Individual
Publication of EP0637483A1 publication Critical patent/EP0637483A1/de
Application granted granted Critical
Publication of EP0637483B1 publication Critical patent/EP0637483B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01R—ELECTRICALLY-CONDUCTIVE CONNECTIONS; STRUCTURAL ASSOCIATIONS OF A PLURALITY OF MUTUALLY-INSULATED ELECTRICAL CONNECTING ELEMENTS; COUPLING DEVICES; CURRENT COLLECTORS
    • H01R43/00—Apparatus or processes specially adapted for manufacturing, assembling, maintaining, or repairing of line connectors or current collectors or for joining electric conductors
    • H01R43/04—Apparatus or processes specially adapted for manufacturing, assembling, maintaining, or repairing of line connectors or current collectors or for joining electric conductors for forming connections by deformation, e.g. crimping tool
    • H01R43/042—Hand tools for crimping
    • H01R43/0427—Hand tools for crimping fluid actuated hand crimping tools

Definitions

  • the invention relates to a tool for machining, in particular pressing workpieces, with a movable machining die and a feed device for its feed movement.
  • Such tools are widely used for pressing sleeves, cable lugs or the like onto a workpiece, but also for cutting, punching or the like.
  • Mainly hydraulically driven tools were used.
  • DE-OS 32 35 0 ⁇ 40 ⁇ discloses a tool in which the processing stamp is moved with the aid of a plunger in which a control element is arranged coaxially. The control member is supported against a gear which is moved when the plunger moves in the working direction of the control member with a fraction of the speed of the plunger.
  • the control element is connected to the plunger in such a way that it moves at the same speed as the plunger.
  • a locking device is arranged on the control member, which blocks the pressure medium flow to the working chamber of the cylinder when the plunger is in a predetermined position. This ensures that thinner workpieces are weaker, d. H. with a lower degree of deformation, are pressed than thicker ones.
  • Another hydraulically operated tool is in the EP-A-0 ⁇ 232768.
  • a low-pressure cylinder and a high-pressure cylinder which can be connected to the pressure medium supply to the tool are provided. These are connected to one another in such a way that in the low-pressure range, with a relatively small number of movements of hand levers that drive the movable piston, a large amount of pressure medium can be conveyed into the working cylinder of the tool in order to produce a rapid feed.
  • the high-pressure pump is used without switching operations being necessary.
  • the high-pressure safety valve can be opened by pressing a release button.
  • the known hydraulic tools all have a relatively complicated structure, the parts coming into contact with the hydraulic oil in particular having to be carried out very precisely.
  • the invention is therefore based on the object of designing a tool of the type mentioned in such a way that it can be manufactured more cost-effectively.
  • the feed device has a coarse feed device for the rapid feed of the processing die to rest on the workpiece and a mechanical fine feed gear for the further feed of the processing die for processing the workpiece, the fine feed gear having defined start and end positions and so with the coarse feed device is coupled so that the fine feed gear is adjusted in the direction of its end position when the coarse feed device is actuated.
  • the fine feed gear is arranged between the rough feed device and the processing stamp, so that the distance between the two can be changed by means of the fine feed gear.
  • This arrangement allows the coarse feed device to be actuated from the end opposite the processing stamp. This does not preclude a reverse arrangement.
  • the invention further provides that the fine feed gear has a release device which becomes effective in the area of the end position and permits a return movement of the processing stamp.
  • This release device can be designed differently depending on the type of fine feed gear and should relieve the fine feed gear and coarse feed device in such a way that the springbacks of the workpiece and widening of the tool that regularly occur during forming processing are taken into account and the workpiece can then be removed from the tool.
  • the Coarse feed device and the processing stamp are coupled parallel to the fine feed gear via a flexible connecting element, the connecting element holding the rough feed device and processing stamp during rapid feed at such a distance that the fine feed gear is disengaged, and wherein the connecting element has such flexibility that the fine feed gear at or after Of the processing stamp on the workpiece engages.
  • the intervention can be frictional or positive.
  • the fine feed gear has a drive and that a switch or a clutch is provided which is controlled when the fine feed gear engages.
  • the fine feed gear can be designed in different ways.
  • a cam track gear can be considered, the cam track not necessarily having to work frictionally, but also having a gear meshing.
  • the cam track gear expediently has a rotatably mounted cam track element with a cam track which has such an incline that when the cam track element is rotated, a fine feed of the processing stamp is effected.
  • the cam track element can be designed as a cam with a cam track on the end face. It should have an indentation at the end of its slope in order to allow the processing stamp to move back in the sense of the release device mentioned above.
  • a stop for the cam track element is provided, which is arranged such that the cam track element moves against the stop during rapid feed and is thereby set in a rotational movement in the direction of its end position.
  • the cam track element should be rotatable from the start to the end position against the action of a spring in order to enable a defined backward rotation.
  • the cam track element can have a drive roller track on which a drive roller bears at least in the engagement position of the fine feed gear.
  • the drive roller conveyor can simultaneously form the cam track.
  • the cam track element is mounted on the processing stamp and the drive roller on the coarse feed device. As an alternative to this, there is the possibility that the drive roller and cam track element are connected to the coarse feed device and the cam track element has a separate cam track for contact with the processing stamp.
  • the fine feed gear has a lever gear connecting a rough feed device and a machining stamp, for example in the form of a crank drive with two articulated arms, the angular position of which can be changed relative to one another.
  • one of the articulated arms has an articulated arm extension which rests against a stop in such a way that the angular position of the articulated arms changes in the direction of their end position during rapid feed.
  • This design also has the consequence that, according to the basic idea of the invention, the residual thrust to be carried out by the fine feed gear is the smaller, the greater the rapid feed with the help of the rough feed device.
  • the articulated connection between the articulated arms has such a guide that the angular position of the articulated arms changes in the direction of their end position during rapid feed.
  • the stop or the guide should be movable via a drive device in the sense of an angle change.
  • the drive device should have a rotatable cam having an incline, the cam having an indentation at the end of its incline. Finally, it should be provided that the angular position of the articulated arms can be changed beyond their extended position in order to achieve a so-called over-center position, with the result that the above-mentioned relief occurs.
  • the tool (1) shown in FIG. 1 has a basic body (2) shown in section and an adjoining tool holder (3) which carries an upper tool (4).
  • a cantilever (5) is a complementary processing punch (6) serving as a lower tool, which is translational, ie. H. guided vertically movable in the selected representation.
  • a rough feed device (7) is arranged in the base body (2) and essentially consists of a vertically guided slide (8) and a spindle (9) with a relatively strong thread pitch.
  • a spindle (9) instead of the spindle (9), other elements such as wedges, cams, etc. are also conceivable.
  • the spindle (9) moves in the direction of its longitudinal axis when it is rotated. Its top tip engages in a suitable recess (10 ⁇ ), where it is supported on the slide (8) via a compression spring (11).
  • a roller (12) is rotatably mounted about a horizontal axis. It is connected to an electric drive, not shown here - mechanical drives are also possible - and protrudes beyond the upper end of the slide (8).
  • the carriage (8) is connected to the processing stamp (6) via a leaf spring (14) which strives to keep both parts at a certain distance.
  • the roller (12) is assigned a fine feed gear (15), to which a cam plate (16) belongs, which is freely rotatably mounted on the processing stamp (6) via a horizontal axis (17) is. On its end face it has a curved path (18), the distance to the axis (17) of which increases continuously upwards. At the end of the curved path (18) there is a flat arch (19). There is a tension spring (20 ⁇ ) articulated, which is connected to the boom (5) and strives to turn the cam (16) clockwise. A stop (21) on the processing stamp (6) limits the movement of the cam disc (16) clockwise.
  • the rough feed device (7), fine feed gear (15) and machining punch (6) are in the initial position with the greatest distance between the upper tool (4) and the machining punch (6).
  • a workpiece (22) - here a cable with a cable lug to be pressed on - can then be inserted into the space between the processing stamp (6) and the upper tool (4).
  • the spindle (9) is then rotated in such a direction that the slide (8) and thus also the machining stamp (6) are moved in the direction of the workpiece (22) at a comparatively high speed.
  • the cam disc (16) comes to rest on a projection (23) after a short distance. With further feed, this projection (23) ensures that the cam disc (16) is pivoted counterclockwise, and the more, the closer the machining stamp (6) approaches the workpiece (22).
  • the spindle (9) can be rotated by such an amount until a shoulder (9a) comes to rest on the slide (8) and there contacts a contact that drives the drive the role (12) switches on.
  • the roller (12) is then rotated clockwise, whereby the cam disc (16) due to the slope of the cam track (18) ensures that the processing punch (6) presses up and the workpiece (22) is deformed. This is only possible with the rest of the curve track (18), the extent of which is smaller the smaller the cross section of the workpiece (22).
  • the spindle (9) is designed so that it acts self-locking, so that the roller (12) can be supported against the spindle (9).
  • the roller (12) moves into the arch (19), whereby the processing stamp (6) is relieved, ie it only bears against the workpiece (23) under the action of the leaf spring (14).
  • the coarse feed device (7) can then be retracted and the workpiece (22) removed.
  • the cam (16) is then turned back to the starting position by the spring (20 ⁇ ). After the spindle (9) has been moved back further, a workpiece can be inserted again.
  • the tool (1) shown in Figure (1) can also be modified in such a way that the roller (12) and the cam disc (16) are interchanged, i.e. the cam disk (16) is mounted on the slide (8) and the roller (12) on the processing stamp (6), the cam disk (16) then being driven.
  • Figures (2) and (3) show a modification of the tool (1) according to Figure (1), the illustration being limited to the design of the fine feed gear (24).
  • the fine feed gear (24) consists of a roller (25) and a circular segment disc (26).
  • the roller (25) is the counterpart to the roller (12) in the tool (1) according to FIG. (1), while the circular segment disc (26) corresponds in its function to the cam disc (16).
  • the circular segment disc (26) has a circular path (27) on the end face with which it rests on the roller (25). It is rotatably and vertically displaceably mounted in a link (29) of the tool (not shown here) via a pin (28). In the area of the pin (28) Circular segment disc (26) has a curved path (30 ⁇ ), on which a processing stamp (31) bears. In addition, the circular segment disc (26) is biased clockwise by a tension spring (32). The circular path (27) has an arch (34) in the area of the tension spring (32).
  • the circular segment disc (26) and thus also the processing stamp (31) are pressed upwards until they come to rest on the workpiece.
  • a stop corresponding to the stop (21) can also be provided here so that the circular segment disc (26) is rotated counterclockwise even during the rapid feed.
  • Figure (3) shows a modification of Figure (2), reference being made to the description according to Figure (2) with regard to the parts of the same design.
  • a circular eccentric path (33) is provided in this case, on which the processing stamp (31) bears.
  • the tool (41) shown in Figures (4) and (5) has a base body (42) which ends in a tool holder (43) which carries an upper tool (44).
  • a processing stamp (45) is mounted displaceably in the base body (42), specifically in the direction of the upper tool (44). It can be used to deform a workpiece (46) when it is moved against the upper tool (44).
  • a coarse feed device (47) is arranged in the lower part of the base body (42) and has a self-locking spindle (49) mounted in a thread (48). This fits into a carriage (50 ⁇ ), which is guided translationally and coaxially to the processing stamp (45).
  • Processing stamp (45) and slide (50 ⁇ ) are connected via a fine feed gear (51), which consists of a crank rod (52) articulated on the processing stamp (45) and a toggle lever (53).
  • the toggle lever (53) has a toggle lever arm (54) which is articulated to the crank rod (52).
  • the toggle lever (52) is mounted on the carriage (50 ⁇ ) via a horizontal axis (55) and has an elongated toggle extension (56). Its free end is pressed by a tension spring (57) against the lower end of a piston rod (58) which is connected to a piston (59), which in turn is vertically movably guided in a hydraulic cylinder (60 ⁇ ).
  • the hydraulic cylinder (60 ⁇ ) is firmly connected to the tool holder (43).
  • the hydraulic cylinder (60 ⁇ ) has a hydraulic input (61) which can be connected to a hydraulic oil supply, for example in the form of a hand pump. There is also a hydraulic outlet (62) which enables the hydraulic oil to return. At the beginning of the hydraulic outlet (62), a vertically movable valve plate (63) is provided, which is acted upon by a compression spring (64). In the position shown, an extension (65) of the piston rod (58) acts on the valve plate (63).
  • the piston rod (58) During rapid feed using the spindle (49), the piston rod (58) remains in the position shown and forms a stop for the toggle extension (56).
  • the valve plate (63) blocks the hydraulic outlet (62).
  • the processing stamp (45) is moved in the direction of the workpiece (46), the toggle lever (53) being pivoted in a clockwise direction due to the abutment on the piston rod (58), as shown in dashed lines. This shortens the remaining stroke of the fine feed gear (51) to its end position, the greater the distance caused by the rapid feed and thus the smaller the cross section of the workpiece (46).
  • the processing stamp (45) reaches the workpiece (46). Since the coarse feed device (47) cannot exert a large force, the rapid feed is then interrupted.
  • FIG (6) shows a further variant of a tool (71) according to the invention in a very schematic representation.
  • the tool (71) has a base body (72), of which only an underside thread (73) and a sliding guide (74) are drawn on the top.
  • a processing stamp (75) is guided so that it can move vertically.
  • an upper tool (76) which is attached to a tool holder (77), which in turn is connected to the base body (72) in a device-fixed manner.
  • a spindle (78) In the thread (73) a spindle (78) is guided, which engages in a carriage (79).
  • the carriage (79) - which is not shown here in more detail - is axially displaceably mounted in the base body (72) in the same way as the carriage (8) in the exemplary embodiment according to FIG. (1).
  • Spindle (78) and slide (79) form a coarse feed device (80 ⁇ ).
  • the processing punch (75) and the slide (79) are connected to two crank rods (82, 83) via a fine feed gear (81), the crank rods (82, 83) being coupled to one another via a joint (84).
  • the joint (84) is supported on a slide (85), which is displaceably guided in the base body (72) transversely to the direction of movement of the processing die (75) or the spindle (78).
  • the slide (85) has an inclined contact surface (86) on the joint side, the inclined position being such that it encloses an acute angle with the axis of the spindle (78) upwards.
  • the slide (85) bears on the rear of a cam disk (87) which is rotatably mounted in a horizontally extending slot (88).
  • a drive pulley (89) is firmly connected to the cam disk (87) and is provided with ratchet teeth (90 ⁇ ) on the end face over part of the circumference.
  • the cam disc (87) and drive disc (89) are supported in the slot (88) via a pivot pin (91) which is spring-loaded via a leaf spring (92) such that the cam disc (87) is pressed against the slide (85) becomes.
  • the elongated hole (88), like the clamping (93) of the leaf spring (92), belongs to the base body (72), without this being shown in more detail here.
  • the drive pulley (89) interacts with a ratchet lever (94), which is brought into contact with a device-fixed stop (96) via a compression spring (95).
  • the ratchet lever (94) is connected in an articulated manner to a hand lever (97) which is connected to the base body (72) via a device-fixed joint (98).
  • a backstop (99) which is pressed against a fixed stop (10 ⁇ 1) by means of a compression spring (10 ⁇ 0 ⁇ ) and thus held in a defined position.
  • the backstop (99) is connected to the base body (72) via a joint (10 ⁇ 2).
  • the tool (71) is operated as follows. First, all parts are in the position shown.
  • the coarse feed device (80 ⁇ ) is then turned by turning the spindle (78) actuated, whereby the machining punch (75) is quickly moved against the workpiece (10 ⁇ 3) resting on the upper tool (76).
  • the joint (84) is supported on the contact surface (86) of the slide (85) and runs up the slope. This has the consequence that the angle between the two crank rods (82, 83) is increased, and the more, the greater the distance traveled with the rough feed device (80 ⁇ ) and thus the smaller the cross section of the workpiece (10 ⁇ 3).
  • the slide (85) remains in the position shown, that is, with the rapid feed, the lateral pressure on the slide (85) is less than the leaf spring (92) acting in the opposite direction on the pivot (91).
  • the drive pulley (89) can be moved clockwise piece by piece by pivoting it in accordance with the double arrow drawn in, clockwise movement of the drive pulley (89) being prevented by the backstop (99).
  • the cam track (10 ⁇ 4) with which it rests on the back of the slide (85) is shaped so that when it is turned clockwise, the slide (85) is moved in the direction of the joint (84).
  • the spindle (78) remains open Because of their self-locking storage in the thread (73) their position.
  • the slide (85) can be moved beyond the top dead center, ie the extended position. Then there is a spontaneous relief, so that the processing stamp (75) can be moved back by means of the rough feed device (80 (). Due to the relief, the leaf spring (92) will move the pivot pin (91) back into the position shown, so that the drive disc (89) comes out of engagement with the ratchet lever (94) and the backstop (99).
  • the cam disc (87), the slide (85) and the crank rods (82, 83) can be moved back until the starting position shown is reached again.

Landscapes

  • Engineering & Computer Science (AREA)
  • Manufacturing & Machinery (AREA)
  • Press Drives And Press Lines (AREA)
  • Turning (AREA)
  • Punching Or Piercing (AREA)
  • Polishing Bodies And Polishing Tools (AREA)
  • Auxiliary Devices For Machine Tools (AREA)
  • Bending Of Plates, Rods, And Pipes (AREA)
  • Hand Tools For Fitting Together And Separating, Or Other Hand Tools (AREA)
  • Shearing Machines (AREA)
  • Feeding Of Workpieces (AREA)
EP94111435A 1993-08-05 1994-07-22 Werkzeug zur Bearbeitung von Werkstücken Expired - Lifetime EP0637483B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4326337 1993-08-05
DE4326337 1993-08-05

Publications (2)

Publication Number Publication Date
EP0637483A1 EP0637483A1 (de) 1995-02-08
EP0637483B1 true EP0637483B1 (de) 1997-09-24

Family

ID=6494547

Family Applications (1)

Application Number Title Priority Date Filing Date
EP94111435A Expired - Lifetime EP0637483B1 (de) 1993-08-05 1994-07-22 Werkzeug zur Bearbeitung von Werkstücken

Country Status (7)

Country Link
US (1) US5720199A (zh)
EP (1) EP0637483B1 (zh)
JP (1) JPH0751774A (zh)
AT (1) ATE158530T1 (zh)
AU (1) AU677400B2 (zh)
DE (1) DE59404141D1 (zh)
NO (1) NO942902L (zh)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FI108924B (fi) * 1997-04-25 2002-04-30 Lillbacka Jetair Oy Menetelmä työstökoneessa
JP2931299B1 (ja) * 1998-07-21 1999-08-09 明邦株式会社 ホッグリング締結装置
US6662620B1 (en) * 2000-09-12 2003-12-16 Black & Decker Inc. Steel stud crimper
US7155955B2 (en) * 2001-09-11 2007-01-02 Emerson Electric Co. Crimping assembly
BR0313551B1 (pt) * 2002-10-18 2014-04-29 Tetra Laval Holdings & Finance Aparelho para perfurar, estampar e/ou conformar elementos planos
CH699050B1 (de) * 2006-06-02 2010-01-15 Fatzer Ag Pressklaue zum Verbinden von Maschen von Drahtgeflechten oder Drahtnetzen, sowie eine Vorrichtung zum Verschliessen der Pressklauen.
CN105889446A (zh) * 2014-09-24 2016-08-24 隆礼湘 车床进给和光学元件位置的粗微调机构

Family Cites Families (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2210510A (en) * 1938-02-22 1940-08-06 Stanley Works Band strapping machine
US2467020A (en) * 1940-01-30 1949-04-12 Chicago Pneumatic Tool Co Compression riveter
NL122121C (zh) * 1960-06-14
US3212316A (en) * 1963-10-23 1965-10-19 Amp Inc Fluid operated crimping tool
US3847007A (en) * 1970-08-11 1974-11-12 T Brownbill Variable throw rocker
CH551264A (it) * 1971-09-02 1974-07-15 Walchhuetter Ulrico Pressa per la produzione di materiali ceramici e refrattari.
US4271710A (en) * 1979-08-07 1981-06-09 Brems John Henry Tool carriage advance and retraction control
US4282739A (en) * 1979-08-08 1981-08-11 N. P. Halenbeck Company Geared power amplification unit for presses
DE3235040C2 (de) * 1982-09-22 1984-12-06 Helmut Dipl.-Ing. 4040 Neuss Dischler Presse zum Aufpressen von Hülsen, Kabelschuhen oder dergleichen
US4559807A (en) * 1983-06-23 1985-12-24 Zavod-Vtuz Pri Moskovskom Avtomobilnom Zavode Imeni I.A. Likhacheva Press
US4646555A (en) * 1985-02-26 1987-03-03 Andrew Postupack Dual stage press
DE3603109A1 (de) * 1986-02-01 1987-08-06 Dischler Helmut Hydraulische handpumpe zum betaetigen von kabelschuhpressen und anderen hydraulischen werkzeugen
US4932237A (en) * 1988-07-21 1990-06-12 Amp Incorporated Portable crimping apparatus
DE3825128A1 (de) * 1988-07-23 1990-01-25 Hilgeland Gmbh & Co Geb Stauchpresse zum stauchen von drahtabschnitten vorbestimmter laenge zu kugeln und dgl.
FR2635285B1 (fr) * 1988-08-12 1990-11-23 Ricard Claude Procedes et dispositifs pour sertir mecaniquement des terminaux sur des fils conducteurs et pour regler avec precision la hauteur de sertissage
JP2534944B2 (ja) * 1991-09-24 1996-09-18 アイダエンジニアリング株式会社 プレス機械
WO1993009911A1 (en) * 1991-11-15 1993-05-27 Yotaro Hatamura Feed screw device and precisely positioning micromotion feed system

Also Published As

Publication number Publication date
NO942902D0 (zh) 1994-08-04
AU677400B2 (en) 1997-04-24
NO942902L (no) 1995-02-06
DE59404141D1 (de) 1997-10-30
ATE158530T1 (de) 1997-10-15
JPH0751774A (ja) 1995-02-28
US5720199A (en) 1998-02-24
AU6876594A (en) 1995-02-16
EP0637483A1 (de) 1995-02-08

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